US11117236B2 - Rotary indexing table with power-optimized drive - Google Patents

Rotary indexing table with power-optimized drive Download PDF

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Publication number
US11117236B2
US11117236B2 US16/637,971 US201816637971A US11117236B2 US 11117236 B2 US11117236 B2 US 11117236B2 US 201816637971 A US201816637971 A US 201816637971A US 11117236 B2 US11117236 B2 US 11117236B2
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United States
Prior art keywords
barrel cam
rotary indexing
indexing table
rotation
drive
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US16/637,971
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English (en)
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US20200230768A1 (en
Inventor
Stefan Bauer
Dominik Goisser
Thomas Andres
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Weiss GmbH
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Weiss GmbH
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Assigned to WEISS GMBH reassignment WEISS GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ANDRES, THOMAS, BAUER, STEFAN, GOISSER, Dominik
Publication of US20200230768A1 publication Critical patent/US20200230768A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q16/00—Equipment for precise positioning of tool or work into particular locations not otherwise provided for
    • B23Q16/02—Indexing equipment
    • B23Q16/022—Indexing equipment in which only the indexing movement is of importance
    • B23Q16/025—Indexing equipment in which only the indexing movement is of importance by converting a continuous movement into a rotary indexing movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/361—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
    • F16C19/362—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single row
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F16H1/166—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel with members rotating around axes on the worm or worm-wheel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q2220/00—Machine tool components
    • B23Q2220/004—Rotary tables
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General buildup of machine tools, e.g. spindles, slides, actuators

Definitions

  • the present invention relates to a rotary indexing table and in particular to a rotary indexing table that is optimized with respect to its required drive power.
  • Rotary indexing tables can be used to rotationally move a workpiece to be machined from a first position of rest into a second position of rest.
  • Such rotary indexing tables are generally known in different embodiments from the prior art and typically have an output flange that is suitable for receiving a workpiece and that is rotatably supported about an axis of rotation at a housing of the rotary indexing table and is drive effectively connected to at least one entrainer that engages into a drive groove of a barrel cam that is drivable by a motor of the rotary indexing table.
  • the output flange thus so-to-say represents a kind of turntable.
  • a rotary indexing table having a barrel cam and in particular the drive effective section (DES; FIGS. 1 b , 2 and 3 ) of the barrel cam, that is defined by the axial extent of the drive groove, is arranged asymmetrically to the axis of rotation of the output flange. It is possible in this manner to optimize and in particular to maximize the effective lever arm length via which the output flange is driven by the barrel cam.
  • the average effective lever arm length during the phase in which the entrainers are conveyed by the drive groove as a result of the rotation of the barrel cam is in particular maximized in comparison with a rotary indexing table having a barrel cam of the same length, but arranged symmetrically.
  • the required drive power and thus the internal friction between the drive groove and the entrainer are thus reduced independently of the respective torque due to the increase of the effective lever arm length in the engagement region so that less torque is required for the drive of the barrel cam.
  • the drive effective section of the barrel cam is offset with respect to an arrangement that is symmetrical with respect to the axis of rotation of the output flange by an amount that approximately corresponds to 5 to 30%, in particular 7 to 25%, of the length of the drive effective section of the barrel cam.
  • Said offset amount can preferably correspond to approximately 10 to 20%, and in particular approximately 15%, of the length of the drive effective section of the barrel cam.
  • the preferred size of the offset amount here depends on the dimensioning of the output flange and of the barrel cam.
  • the offset amount in particular depends on the radius of the barrel cam, on the pitch of the drive groove, and on the number of entrainers and their radial spacing from the axis of rotation of the output flange.
  • the output flange can be supported at the housing of the rotary indexing table by means of a ball bearing supported slewing ring.
  • the support of the output flange by means of a ball bearing supported slewing ring at the housing of the rotary indexing table can here be used additionally or alternatively to the asymmetrical arrangement of the barrel cam in accordance with the first aspect of the invention.
  • the ball bearing supported slewing ring can here preferably be designed as an eight point bearing or as a cross roller bearing.
  • the support of the drive flange in conventional rotary indexing tables takes place via combinations of axially and radially effective bearings. Since the bearing friction of ball bearing supported slewing rings is as a rule smaller than the bearing friction of combined axial and radial bearings, the required drive power can be further reduced by the support of the output flange by means of a ball bearing supported slewing ring at the housing of the rotary indexing table.
  • FIGS. 1 a -1 c show an embodiment of a rotary indexing table in accordance with the invention in different views;
  • FIG. 2 illustrates the effective lever arm relationships of a conventional rotary indexing table having a symmetrically arranged barrel cam
  • FIG. 3 illustrates the effective lever arm relationships of a rotary indexing table in accordance with the invention having an asymmetrically arranged barrel cam.
  • FIG. 1 a perspectively shows a rotary indexing table 10 in accordance with the invention that in the embodiment specifically shown here has an annular output flange 12 formed as a turntable 11 to receive workpieces to be machined (not shown).
  • the output flange 12 or the turntable 11 is here supported rotatably about an axis of rotation A at a housing 14 of the rotary indexing table 10 so that the output flange 12 can be rotationally moved from one position of rest into a second position of rest.
  • the output flange 12 is annular and surrounds a central opening 16 in which, for example, one or more machining tools (not shown) can be located to machine workpieces located on the turntable 11 .
  • the rotary indexing table 10 or its output flange 12 is driven by a motor, not shown here, whose shaft can be coupled to a drive shaft 18 of the rotary indexing table 10 .
  • the drive shaft 18 here drives a barrel cam 20 that is rotatably supported in the housing 14 of the rotary indexing table 10 .
  • a spirally peripheral drive groove 22 is formed in the barrel cam 20 and the entrainers 24 that are drive effectively connected to the drive flange 12 at its side that is lower—in the position of use—engage into said drive groove 22 .
  • the entrainers 24 are here designed as roller pins having cam rollers 26 . The entrainers 24 engaging into the drive groove 22 are thus dragged along by the rotational movement of the barrel cam 20 , whereby the output flange 12 is driven to make a rotational movement in the desired manner.
  • the output flange 12 is supported in accordance with the invention by means of a ball bearing supported slewing ring 28 designed as a four point bearing at the housing 14 of the rotary indexing table 10 , whereby the bearing friction can be minimized in the desired manner in favor of the reduction of the required drive power for the rotary indexing table 10 .
  • the drive effective section of the barrel cam 20 is here offset with respect to an arrangement that is symmetrical with respect to the axis of rotation A of the output flange 12 by an offset amount V that approximately corresponds to 15% of the length of the drive effective section of the barrel cam 20 .
  • the specific offset amount V depends on the geometry of the respective rotary indexing table and is preferably in the region between 10 and 20% of the length of the drive effective section of the barrel cam 20 .
  • FIG. 2 here explains the effective lever arm length in a conventional rotary indexing table 10 ′ having a symmetrically arranged barrel cam 20 ′ as is schematically illustrated in the left hand representation of FIG. 2 .
  • the right hand representation of FIG. 2 here illustrates the effective lever arm length in dependence on the angle of rotation of the output flange, that is not shown here.
  • the individual entrainers 24 ′ enter into the drive groove 22 ′ of the barrel cam 20 ′ at an angle of rotation ⁇ of approximately ⁇ 31°, whereupon they are dragged along by the drive groove 22 ′ as a result of the rotational movement of the barrel cam 20 ′ and exit the same again at an angle ⁇ of approximately 31°.
  • the effective lever arm length here increases during this engagement region from a starting value of approximately 270 mm to a maximum value of approximately 275 mm before the effective lever arm length subsequently continuously reduces down to a minimal lever arm length of approximately 190 mm at that point in time at which the entrainers 24 ′ leave the drive groove 22 ′ again.
  • the effective lever arm length can be determined here in that the radial spacing of the respective entrainer 24 ′ from the axis of rotation A at every angle of rotation ⁇ of the output flange is split into two vectors which are perpendicular to one another and of which the one vector is perpendicular on the border of the drive groove 22 ′. The other vector then represents the effective lever arm length.
  • the minimal effective lever arm length is thus 40 mm larger (230 mm with the asymmetrically arranged barrel cam with respect to 190 mm with a symmetrically arranged barrel cam), whereby the maximum strain on both the entrainers 24 and the barrel cam 20 can be reduced. Due to the larger minimal effective lever arm length, less torque is furthermore also required for the drive of the output flange 12 , whereby the drive power required for the drive of the rotary indexing table 10 can be minimized.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Machine Tool Positioning Apparatuses (AREA)
US16/637,971 2017-08-10 2018-07-17 Rotary indexing table with power-optimized drive Active US11117236B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102017118262.4A DE102017118262A1 (de) 2017-08-10 2017-08-10 Rundschalttisch mit kraft-optimiertem antrieb
DE102017118262.4 2017-08-10
PCT/EP2018/069338 WO2019029953A1 (de) 2017-08-10 2018-07-17 Rundschalttisch mit kraft-optimiertem antrieb

Publications (2)

Publication Number Publication Date
US20200230768A1 US20200230768A1 (en) 2020-07-23
US11117236B2 true US11117236B2 (en) 2021-09-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
US16/637,971 Active US11117236B2 (en) 2017-08-10 2018-07-17 Rotary indexing table with power-optimized drive

Country Status (11)

Country Link
US (1) US11117236B2 (pl)
EP (1) EP3641983B1 (pl)
KR (1) KR102560031B1 (pl)
CN (1) CN111050997B (pl)
BR (1) BR112020002825A2 (pl)
CA (1) CA3072531A1 (pl)
DE (1) DE102017118262A1 (pl)
DK (1) DK3641983T3 (pl)
ES (1) ES2890950T3 (pl)
PL (1) PL3641983T3 (pl)
WO (1) WO2019029953A1 (pl)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021090551A1 (ja) * 2019-11-08 2021-05-14 株式会社三共製作所 回転位置決め装置
JP7490233B2 (ja) * 2020-10-19 2024-05-27 テクノダイナミックス株式会社 減速機
DE102023108594A1 (de) * 2023-04-04 2024-10-10 Weiss Gmbh Abtriebsflansch für einen rundschalttisch zur aufnahme eines werkstücks sowie rundschalttisch mit solch einem abtriebsflansch

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DE102006061310A1 (de) * 2006-12-22 2008-07-03 Tünkers Maschinenbau Gmbh Vorrichtung zum Bewegen von Massen mittels einer Welle, die über einen motorischen Antrieb, ggf. mit unterschiedlichen Winkelgeschwindigkeiten antreibbar ist, und Verwendung einer derartigen Vorrichtung bei einem Drehtisch mit Schrittantrieb
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DE102008060569A1 (de) 2008-12-04 2010-06-10 Schaeffler Kg Lageranordnung mit Magnetlagerabschnitt sowie Verfahren zur Regelung einer oder der Lageranordnung
DE102010016682A1 (de) 2009-04-29 2010-11-04 Avl List Gmbh Verfahren zur dynamischen Totzeitkompensation der Abgaskonzentration
EP2255923A1 (de) 2009-05-28 2010-12-01 WEISS GmbH Rundschalttisch
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US10646974B2 (en) * 2017-11-28 2020-05-12 Kuo Ming Chen Indexing device

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Publication number Priority date Publication date Assignee Title
DE150839C (pl)
FR2248745A5 (en) 1973-10-22 1975-05-16 Nussle Lionel Variable speed drive mechanism - has spiral strip on gear drum which drives rollers fitted onto gear wheel
JPH01252342A (ja) * 1988-03-31 1989-10-09 Sankyo Seisakusho:Kk 間欠割出し装置
US5188004A (en) * 1988-12-21 1993-02-23 Kabushiki Kaisha Komatsu Seisakusho Turntable apparatus for universal machine tool
US6279219B1 (en) * 1998-09-24 2001-08-28 Takahiro Engineering Works Ltd. Roller turret including rollers mounted on support portions of roller shafts, which are eccentric with respect to stud portions fixed in holes in turret body, and method of manufacturing the roller turret
US6862786B2 (en) * 2000-10-25 2005-03-08 Sankyo Manufacturing Co., Ltd. Rotating table apparatus
US20060013519A1 (en) * 2002-12-16 2006-01-19 Masafumi Fukunaga Four-point contact ball bearing
CN1608795A (zh) 2003-10-17 2005-04-27 株式会社三共制作所 夹紧装置和旋转工作台设备
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DE202004006697U1 (de) 2004-04-25 2005-03-31 Glatz Dietmar Rundtischlager
US7603930B2 (en) * 2004-10-15 2009-10-20 Sankyo Seisakusho Co. Rotary table apparatus
DE102006061310A1 (de) * 2006-12-22 2008-07-03 Tünkers Maschinenbau Gmbh Vorrichtung zum Bewegen von Massen mittels einer Welle, die über einen motorischen Antrieb, ggf. mit unterschiedlichen Winkelgeschwindigkeiten antreibbar ist, und Verwendung einer derartigen Vorrichtung bei einem Drehtisch mit Schrittantrieb
DE102008060569A1 (de) 2008-12-04 2010-06-10 Schaeffler Kg Lageranordnung mit Magnetlagerabschnitt sowie Verfahren zur Regelung einer oder der Lageranordnung
DE102010016682A1 (de) 2009-04-29 2010-11-04 Avl List Gmbh Verfahren zur dynamischen Totzeitkompensation der Abgaskonzentration
EP2255923A1 (de) 2009-05-28 2010-12-01 WEISS GmbH Rundschalttisch
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DE102013109307A1 (de) 2013-08-28 2015-03-05 Taktomat Kurvengesteuerte Antriebssysteme Gmbh Drehtisch
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DE102015224865A1 (de) * 2015-12-10 2017-03-09 Schaeffler Technologies AG & Co. KG Rundtischlager
DE102015224860A1 (de) * 2015-12-10 2017-03-16 Schaeffler Technologies AG & Co. KG Rundtischlageranordnung
US10646974B2 (en) * 2017-11-28 2020-05-12 Kuo Ming Chen Indexing device

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First Chinese Office Action, along with an English translation, dated Jun. 2, 2021 for Chinese Application No. 201880049960.3, 7 pages.
Machine translation of DE 102015224860 A1 obtained on May 21, 2020. *
Official Communication from the European Patent Office for related International Application No. PCT/EP2018/069338; dated Jan. 4, 2019; 5 pages.
Official Communication from the German Patent Office for related German Application No. 102017118262.4; dated May 9, 2018; 2 pages.

Also Published As

Publication number Publication date
CN111050997A (zh) 2020-04-21
WO2019029953A1 (de) 2019-02-14
KR20200042909A (ko) 2020-04-24
CN111050997B (zh) 2022-08-09
EP3641983A1 (de) 2020-04-29
EP3641983B1 (de) 2021-09-08
US20200230768A1 (en) 2020-07-23
PL3641983T3 (pl) 2022-02-07
DK3641983T3 (da) 2021-10-11
KR102560031B1 (ko) 2023-07-25
BR112020002825A2 (pt) 2020-08-04
CA3072531A1 (en) 2019-02-14
DE102017118262A1 (de) 2019-02-14
ES2890950T3 (es) 2022-01-25

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